Pump liner



May 21, 1963 H. M. STANLEY PUMP LINER 6 Sheets-Sheet 1 Filed June 30, 1961 I N V EN TOR. HsuomswMwaewaSmw /-//.sA rraeus v May 21, 1963 H. M. STANLEY PUMP LINER 6 Sheets-Sheet 2 Filed June 30, 1961 INVENTOR. I /ENDERJoMMUSGKa vzSmuur H/s A 1' TOEHEY Ln v y 1963 H. M. STANLEY 3,090,319

PUMP LINER Filed June 30, 1961 6 s s 3 Fig.3

IN V EN TOR. Haws/2.5 ONMUSG'RO v5 57% AIL EY H/J A TTOENEY May 21, 1963 H. M. STANLEY 3,

PUMP LINER Filed June 30, 1961 6 Sheets-Sheet 5 Fig.7

INVENTOR. HEHDERSONMUSGKOVE STANLEY May 21, 1963 H. M. STANLEY PUMP LINER 6 Sheets$heet 6 Filed June 30, 1961 INVENTOR. HENDERSOHMUSGEOVESTANLEY B flwym H sArroRA/Ev United States Patent 3,099,319 PUMP LINER Henderson Musgrove Stanley, Fairmont, W. Va., assignor to Helmick Foundry-Machines Company, Fairmont, W. Va., a corporation of West Virginia Filed June 30, 196i, Ser. No. 121,038 11 Claims. (Cl. 103-103) This invention relates generally to fluid machines such as blowers and liquid pumps and more particularly to a removable annular liner to withstand the abrasion of products carried through such fluid machines.

The problem in blowers and pumps and other fluid machines is the provision of a removable liner that may be quickly removed and replaced to avoid extended loss of the service of the fluid machine. If the housing, whether it is lined or not, wears due to erosion it is necessary to replace the whole machine. This requires the removal of the drive couplings or the motor drive together with the fluid machine in order to repair the same. It not only takes time but the next machine frequently requires different mounting =blocks because it is of a different style, make, or is changed to require the replacement to be tailor fitted when installed. Even a stand-by machine of the same make and style creates problems because of slight differences. When fluid machines of this character are mounted to supply a continuous service, such as the removal of quenched ash from the combustion chamber, this has to be continuously sluiced away or irreparable damage may be caused by failure to remove as well as mere loss in efliciency.

These problems are'overcome by the provision of a fluid machine having a removable liner. The liner of fluid machines comprising this invention is preferably a partible liner than can readily be replaced without even uncoupling the impeller drive or the inlet or the outlet connections. By retaining the driving connection this invention provides a novel and quick mode of removing a worn and inefiicient volute lining by merely unbolting and removing the top half of the housing. The top half of the housing has a flat flange connection to the bottom half and may contain the outlet, which permits the liner to be slipped out when the housing is unbolted and removed. The top liner is withdrawn from the top half of the housing and the bottom half of the liner may be rotated or slid around from under the impeller and replaced.

If the outlet throat is in the bottom or stand half of the housing, the housing may be separated through the outlet.

The liner halves may he slid around from under the impeller by merely unbolting and removing the top half of the housing and the top section of the liner if the inner annular surface of the housing is circular. This is true when the housing has sufficient clearance for the liner, regardless of whether the outer perimetral surface of the liner follows the volute curve or follows a circular path. If the housing follows a volute curve one merely slides the liner toward the largest diameter under the impeller to the top to remove the same.

The liner comprising this invention is preferably partiole in radial planes which may or may not coincide with the parting of the housing. The housing is preferably made in two parts and separated along one straight plane with the liner split along the same plane. The liner may be split in three or more parts, the planes of which are radial. However in the preferred form the liner is split along the same straight plane as the housing and the liner part is shaped so that it may be slid around in the housing from under the impeller.

Fluid machines of this character preferably have volute ice chambers. The liner comprising this invention thus has the involute formed therein. If it is allowed to Wear until it has put a hole in the liner and also the housing, the latter may be welded or patched and a new liner slipped in place, which provides a relatively new pump without removal, which cannot be accomplished with the present fluid machines.

The liner comprising this invention is provided with an annular perimetral wall forming a chamber to receive and guide the fluid impelled radially by the impeller. It is also provided with annular inturned flanges that extend on one side to the shaft seal support and on the other side to the inlet or vortex of the impeller. These flanges being an integral part of the liner provide an assurance that no part of the casing is eroded by the fluid circulated through the operating chamber. These liner parts are readily replaceable and the fluid machine may be kept operating at maximum efliciency by periodically changing the liners. Fresh water is supplied to the liner flanges and the impeller surfaces provide a natural centrifugal pump surface when coacting with the outer circular wall of the impeller and thus avoid wear by the eroding fluid returning toward the rotary axis clue to the radial flow of the fresh water.

The liner with the side flanges permits an improved structural form of liner wherein the perimetral portion that collects the flow stream from the radial discharge of the impeller may be made thick and heavy, whereas the flanges which are not subjected to this wear may be thinner and light. The material making up the liner may be stone, glass, plastic, an elastomer, a metal such as chrome, nickel, steel, stainless steel, mild steel cladded with stainless copper, aluminum, or cast steel, or iron, chrome nickel cast iron or other suitable materials. The latter is successful for fluid machines transporting a slurry of ash which is abrasive. Thus in forming these liners by drawing, cutting, forging, or casting, the correct shapes may be made accurately to place the heavy walls where needed and form the flanges with thinner walls where wear is not prevalent.

Another object is the provision of a seat on the interior of the housing which cooperates with seats on the liner parts and holds them properly in the housing when the latter is clamped together. This is accomplished with the use of mating flanges secured by flange clamping I bolts together with a gasket of selected thickness and quality which when squeezed between the parting flanges of the housing will compress and permit a clamping force to be applied through the seat on the housing and hold the liners in place. The gasket also seals and supports clamping pressure between the flanges, thus limiting the pressure applied to the liner parts. These seats may be inner annular surfaces on the housing that engage the liner when the housing is bolted along radial planes passing through the axis of rotation. Again these seats may be spaced seats on the shaft side or" the housing and the flange, gasket and bolts secure the inlet member and move its shoulder against the liner to seat the same axially against the spaced seats on the shaft side of the housing. Thus the liner may be properly seated axially and transversely of the rotary axis and properly held in place by three diiferent structures and any one of them is suflicent to properly locate and hold the liner.

This improvement also contemplates the provision of a tubular inlet that is secured to the housing and extends into the liner flange and toward the vortex of the impeller. This not only insures undisturbed flow past the split liner to the impeller vortex but has an abutment to engage the side of the flange and seat i-t axially as previously stated.

Another object is the provision of a bell housing in the inlet side of the housing that is merely boxed in by the liner. In liquid pumps, fresh water is supplied on the shaft side to the housing and leaks past a wiper and around the outer perimetral surface of the liner to this annular ofiset or bell chamber. Thus fresh clean water is actually circulated past the seats and around the liner. The water flows under each of the annular flanges of the liner to get to the operating chamber on both sides of the liner and also to the vortex on the inlet side. This offset or bell chamber has a different purpose when the fluid machine is opened. By removing the top half of the housing and both halves of the liner, the impeller may be loosened and unscrewed from the shaft and moved into this chamber. The inlet tubular member is withdrawn and the impeller is removed from the housing by merely lifting it up and out.

An alternate wayof removing the impeller is by providing a thick coupling in the shaft which when withdrawn from the impeller the latter may be raised from .the housing without the need of the annular offset charnber in the housing and without withdrawing the tubular inlet or the bottom half of the liner. Thus the lower housing section and any other connections need not be disturbed to rebuild the pump or blower and anyone may install a new liner and replace the impeller.

Another object is the provision of an offset on each side of the operating chamber formed by the liner in which to receive the disc sides of the impeller. By overlying these cylindrical surfaces of the impeller disc sides the liner protects them from eroding. Thus properly selecting the material for the impeller and the liner so that they match each other in wear, both requiring replacement at the same time, provides economy in oper- .ation.

Another object is the provision of an overhang at the perimetral section of the liner parts in the direction of rotation of the impeller to reduce the friction of the circulating fluid as it travels from one volute section of the liner to the other.

Other objects and advantages of this invention appear hereinafter in the following description and claims.

The accompanying drawings show for the purpose of exemplification without limiting this invention or the claims thereto, certain practical embodiments illustrating the principles of this invention, wherein:

FIG. 1 is a view in side elevation with parts in section illustrating this invention.

FIG. 2 is a view in transverse section illustrating the fluid machine.

FIG. 3 is an end view of the structure shown in FIG. 1.

FIG. 4 is a view in horizontal section with the upper half of the housing moved.

FIG. 5 is a perspective view of the rotor socket for receiving a threaded shaft.

FIG. 6 is a perspective view of the rotor shaft nut.

FIG. 7 is a view in transverse section illustrating a modified form of the fluid machine.

FIG. 8 is a view in side elevation with parts thereof in section of a fluid machine without a liner illustrating one phase of this invention.

FIG. 9 is a view in side elevation with parts in section illustrating a further modification of this invention.

Referring to FIG. 1, the fluid machine 1 comprising this invention depicts a centrifugal liquid pump having a dual housing, the lower section 2 provided with feet 3 and mounted thereon is the upper housing section 4 which is split along a plane or medial line extending through the rotary axis. The medial line of each housing section is defined by the lower and upper flanges 5 and 6 which receive therebetween the duplicate gasket sections 7. Each housing section is provided with semicircular seats 8 and 10 on the inlet side of the pump which produces a complete annulus as illustrated in FIG. 1 upon which is mounted a gasket 11. The annulus formed by the surfaces 8 and 10 receives the flange 12 of the inlet housing 13 which has a frusto conical bore 14 and an external annular seat 15. The inlet spool 16 is also provided with a mating frusto conical bore 17 and is provided with end flanges 18 and 20, the flange 18 being secured with a gasket member 21 and the flange 12 to the lower member housings 2 and 4 by the bolts 22 which are secured in the threaded openings 23 of the annulus formed by the surfaces 8 and 10 as shown in FIG. 1. The flange is also provided with bolt slots for securing the inlet spool 16 to a line or other source of fluid to be pumped.

As shown in FIG. 1, the opposite sides of the pump housing sections 2 and 4 are provided with a semicircular surface 23 and 24 on which is placed the gasket 25 and the annular shaft seal supporting member 26 having an annular flange 27 which is secured to the housing sections 2 and 4 by the bolts 28.

The seal supporting member is provided with a bore to receive the shaft 3t? and an enlarged bore forming the stufling box 31 having a threaded gland member 32. The shaft member extends into the housing and is provided with a recess for receiving the locking ring 33 outwardly of the groove holding the locking ring 33. The shaft is threaded as illustrated at 34 which is received in the threaded opening 35.

Referring now to FIGS. 1, 5 and 6, the nut 36 has a plurality of bayonet locking flanges 37 the end of which bayonet locking flange terminates in an axial recess 38 as shown in FIG. 6.

As illustrated in FIG. 5 the socket 40 in the impeller 41 has corresponding axial slots 42 and adjacent underlying pockets 43 for receiving the bayonet locking flanges 37 of the nut 36. When the nut is inserted to its full depth it is turned in the direction of the arrow which is equivalent to the direction of rotation of the pump and these bayonet locking flanges slide into their corresponding pockets 43 to become jammed. When the nut 36 has been centered in the socket 4t and in proper balanced relation relative to the impeller the nut is leaded in by inserting lead or babbitt through the grooves 38, thereby locking the nut in position.

The shaft 30 extends through the aligned split bearings 44, 45, 46 and -47 mounted in the bearing stand 48 and the bearing cap 50. The end bearings 44 and 47 are retained directly between the stand and cap. However the intermediate bearings and 46 are retained within the split sleeve member 51 the intermediate sec-tion of which is enlarged as indicated at 52 to receive the outer races 53 spaced by the abutment mem- -ber 54. The corresponding inner races 55 are properly seated against the fixed shoulders 56 and the movable shoulder 57 of the shaft 30. These are the well known conical bearings receiving the thrust load imposed on the impeller 41.

In order to properly locate the impeller 41 in the housing sections 2 and 4 mechanical adjustment such as illustrated at '60 may be employed which consists in a nonround member 61 in the center of the stud 62 that has threads of opposite hand at either end which are received in corresponding threaded sockets 63 and 64 on the bearing stand 48 and the lower housing section 2. Thus by rotating the nonround portion 61 the pump housing is moved axially in either direction to properly locate the impeller 41 in the housing. Any suitable adjusting means can be employed for this purpose.

Referring specifically to FIGS. 1 to 4, the interior of the housing sections 2 and 4 is provided with an annular chamber 65 in the form of a volute commencing at 66 and terminating at the point of tangency 67. This chamber terminates on the axially disposed annular seats 68 and 69 on opposite sides of the chamber 65 and which define the same.

On the shaft side of the housing sections 2 and 4 extend the annular surface 23 that faces the flange 25 and is provided with a bore provided with a sliding fit for the cylindrical portion 70 of the seal supporting member 26.

On the opposite side of the chamber 6g the housing sections 2 and 4 extend axially as illustrated at 7 1 to provide the bell chamber 72 and terminate in the annulus 73 which also provides a sliding fit with the inlet member 13.

The liner 74 follows substantially the shape of the chamber 65 to provide the annular volute chamber 75. On each side of the chamber the liner extends axially to provide the seats 76 and 77 which correspond and match with the seats 68 and 69 of the housing. These are matched seating surfaces through which pressure is applied by the clamping bolts 78 which compress the gasket 7 to permit a predetermined pressure transmitted through the corresponding seats 68 and 76 and 69 and 77 to clamp the liner 74 in its proper position in the housing.

The liner 74 is preferably made in two sections 80 and 81 which are ground along the same plane as the housing and defined as a plane in which the gasket 7 occupies.

The gasket 7 is chosen to permit a predetermined pressure to be transmitted through the seats 68 and 7-6 and 69 and 77 between the housing and the liner not only to properly seat the liner but hold the liner halves in tight mating engagement in a single transverse medial line or split 79. Thus the annular seats and the engaging surfaces of the two liner sections are ground so as to properly seat under clamping pressure and prevent leakage.

The shaft side of the lower and upper housing is provided with spaced annular pads 82 and 83 and the corresponding surfaces on the liner 74 are likewise ground to flt the pads. Thus by selecting a predetermined gasket 11 under the flange 12 of the inlet member 13' the bolts 22 will supply sufficient pressure through the shoulder 15 to the annular flange 84 of the liner 74 to move the liner axially until it seats on the pads '82 and 83, thereby moving the liner relative to the housing and to the impeller 41 which has been adjusted relative to the housing.

As an alternative of applying axial force to the liner 74 a series of four bolts 85 are threadably received in openings of the housing sections 2 and 4 and abut the liner 74 axially until it seats against the annular pads 82 and 83. The washer '86 is placed under the bolt head 85 to seal the same. Thu-s we provide two methods for pre-positioning the liner 74 within the housing.

As shown in FIGS. 2 the opposite sides of the liner sections '80 and 81 along their medial split 79 will overlie the next adjacent portion of the volute chamber 75 as illustrated by the overhang 87 on the left of FIG. 2 and the overhang 88 on the right of FIG. 2 in the direction of travel of the liquid fluid, which in this instance is counterclockwise as produced by the blades 90 of the impeller 41 which connect the discs 91 and 92 on opposite sides of the impeller 41. Spaced between the blades is connected the vortex 93 of the impeller which is slightly larger than the increasing frusto conical bore 14 of the inlet.

A vane made in two sections 94 and 95 depends fro-m the top frusto conical bores of the inlet members 13 and 16. These vanes constitute a single Vane to prevent prerotation of the fluid into the inlet due to suction of the vortex. These vanes are pre-aligned as are the housing parts with dowel pins.

The cylindrical surfaces defining the perimeter of the impeller discs 91 and 92 are covered by the offsets $6 and 97 on each side of the liner 74.

The seal supporting member 26 is provided with a fluid inlet 98 for receiving a supply of fresh water at pressure which is materially higher than the pressure produced by the pump and which seeps under the wiper i and may flow past the notches 100 at the joints between the two liner sections so as to flow upwardly around the outside of the liner to fill the bell shaped offset chambers 72 and flow outwardly to the vortex of the pump. Water also seeping past the wiper 9% will flow radially outwardly between the disc 92 of the impeller 41 and the inner face of the liner which produces a centrifugal pump action in flowing the fresh water radially outwardly across the offset 97 to the volute chamber 75. This maintains the exterior of the liner clean and prevents dirt, corruption or abrasives from reaching the packing gland 3 1.

As shown in FIG. 7, the housing sections 102 and 16 1 are split radially along the diameter 103 to the center of the outlet 104 and are bolted together by means of the bolts 78. The liner 74 is the identical liner to that shown in FIGS. 1 to 4 having the sections "81 divided at '79. Here when the outlet 104 is formed in the bottom section of the housing having the feet 105 the split is merely relocated.

Referring to FIG. 8 the structure therein shown is the same as that illustrated in FIG. 1 with the exception that the liner 74 has been removed and. the diameter of the impeller discs 91 and 92 is slightly increased. The diameter of the chamber 72 is the same size.

In each of the structures as shown in FIGS. 1 and 8 if the upper housing section 4 of the housing is. removed the upper section 80 of the liner may be removed in FIG. 1 and then the lower section 81 may be rotated in a counterclockwise direction so as to ride under the impeller 41 until it comes out of the open top where it can be removed.

The shaft 30, which is the drive, prevents the impeller from being rotated, and by placing a bar between the blades 98' of the impeller one can unscrew the impeller 41 from the shaft 36 as the impeller unscrews from the shaft 30 which is held against axial movement. The impeller moves to the lift in these views until it occupies the chambers 72 at which time it is completely unthreaded from the shaft 3%. If the inlet sections 16 and 13 are removed from the housing then the impeller in poth structures of FIGS. 1 and 8 may be raised vertically out of the housing chamber without otherwise dismantling the lower section of the housing and its relation to the bearing stand 43. Thus one can replace either the impeller 41 in FIG. 8 or the impeller 41 and both line sections 8%) and 81 in FIG. 1 Without disrupting or otherwise disengaging the rest of the mechanism. In this manner the pump can be completely rebuilt in a very short period of time.

Referring now to FIG. 9, it will be noted that the chamber 72 has. been eliminated from the housing members 2 and 4 and the cross section of these housing sections follow substantially the shape of the liner 74.

The shaft is divided into sections 3% and as and is provided with a coupling having a removable intermediate section 106 that may be completely removed without disturbing the thrust bearing 167. When the section 106 is removed that portion of the shaft 30 attached to the impeller 41 may be unscrewed from the impeller and as it unscrews from the impeller it moves to the right in FIG. 9 until it clears, after which time the impeller may be raised vertically out of the lower section 2 of the housing when the upper section 4 is removed. Otherwise the pump structure is the same. The bearings 44 and 45 merely support the shaft section 39', whereas the bearings 46 and 107 support the shaft section 30.

I claim:

1. A centrifugal fluid pump consisting of a two-part annular housing with integral radial flanges and having an axial inlet and a circumferential discharge connected to an outlet, said housing with its flanges partible along a single medial transverse line with pressure exerting means to secure the parts together, a rigid two-part annular liner having integral radial flanges removably mounted in said housing to form a pump chamber defined by a complementary circumferential discharge and an impeller en- 7 closure, said liner with its flanges partible along the same medial transverse line as said housing, said liner flanges forming the sides of said impeller enclosure and on one side circumscribing the inlet thereto, cooperating complementary seats located on opposed surfaces on each housing and liner part between each flange and its circumsurfaces of the radial discharge sides of said impeller, one

of said liner parts being removable from around said mounted impeller when the other part of said liner and housing are removed from said medial transverse line.

2. The fluid pump of claim 1 which also includes a horizontal offset between the circumferential discharge and each flange on both of said housing and liner parts, each offset carrying said seats and overlapping the perimetral edges of the sides of said impeller.

3. The fluid pump of claim 1 characterized in that said pressure exerting means operating through said seats in said housing and liner parts also includes gasket means for insertion along said medial transverse line between the housing parts to determine the clamping pressure on said partible liner, and bolts to clamp said housing parts and said gasket means therebetween to seal said housing parts along said medial transverse line and to seat and hold said partible liner parts together.

4. The fluid pump of claim 1 which also includes an inlet member in the form of an independent tubular inlet liner secured to and covering said housing inlet and extending toward the vortex of said impeller and overlying said liner flange on the inlet side of said-pump, an annular shoulder on said inlet liner to engage said partible liner flanges on the inlet side of said pump and seat said liner parts against the opposite side of said housing.

5. The fluid pump of claim 1 characterized in that the wall surfaces at the perimetral junction of said liner parts along said medial transverse line overhang into said pump chamber and in the direction of rotation of the impeller to reduce the friction of the circulating fluid at this junction.

6. The fluid pump of claim 1 which also includes axial pressure exerting means on said housing flange on the inlet side of said pump to bear against the corresponding liner flange on the same side of said pump, and pads between the opposing flange surfaces of said housing and liner on the opposite side of said pump to seat said liner axially relative to said impeller.

7. The fluid pump of claim 6 wherein said axial pressure exerting means are bolt means on said housing flange hearing against said corresponding liner flange adjacent the juncture where the latter flange is integral with its circumferential discharge.

8. The fluid pump of claim 1 characterized by a shaft, means detachably connecting one side of said impeller to said shaft, a bell in said housing on the side opposite 8 said means detachably connecting said impeller to said shaft to provide for axial movement of said impeller into said bell of said housing when detached from said shaft to permit said impeller to be lifted free of said housing When one part of said housing and liner are removed and Without disturbing said shaft.

9. The fluid pump of claim 8 characterized in that said liner part flanges on one side of said impeller cover said bell in said housing, said one liner part being removable slidably from around said mounted impeller to expose said bell ton enable the lateral movement of the detached impeller for removal from said fluid pump.

10. A fluid pump consisting of a two-part housing partible along a medial transverse line and mounted for operation to form a chamber having an outlet, an axially removable inlet on said housing, a radially discharge impeller mounted for rotation in the housing chamber on the side opposite to said inlet, said chamber receiving the radial discharge from said impeller to convey it to said outlet, a drive shaft, means detachably connecting said impeller from said drive shaft to permit said impellers removal from said housing with one housing part removed, a support for said housing, a bearing support for said drive shaft, an annular bell in said housing on the side opposite to said means detachably connecting said impeller from said drive shaft to provide for axial movement of said impeller in the housing when disconnected by said detachably connecting means and to permit said impeller to be lifted free of said housing when opeend by the removal of one housing part and said axially removable inlet without disturbing said drive shaft or said supports.

11. A fluid pump consisting of a two-part housing 'partible along a medial transverse line and mounted for operation to form a chamber having an outlet, an axially removable inlet on said housing, a radially discharge impeller mounted for rotation in the housing chamber on the side opposite to said inlet, said chamber receiving the radial discharge from said impeller to convey it to said outlet, a drive shaft, means detachably connecting said impeller from said drive shaft to permit said impellers removal from said housing with one housing part removed,

I a support for said housing, a bearing support for said drive shaft, a coupling in said drive shaft, a removable intermediate section in said coupling to provide for axial movement of a short section of said shaft from said impeller when detached from the latter to permit said impeller to be lifted from said housing with one housing part removed and without disturbing said supports.

References Cited in the file of this patent UNITED STATES PATENTS 

1. A CENTRIFUGAL FLUID PUMP CONSISTING OF A TWO-PART ANNULAR HOUSING WITH INTEGRAL RADIAL FLANGES AND HAVING AN AXIAL INLET AND A CIRCUMFERENTIAL DISCHARGE CONNECTED TO AN OUTLET, SAID HOUSING WITH ITS FLANGES PARTIBLE ALONG A SINGLE MEDIAL TRANSVERSE LINE WITH PRESSURE EXERTING MEANS TO SECURE THE PARTS TOGETHER, A RIGID TWO-PART ANNULAR LINER HAVING INTEGRAL RADIAL FLANGES REMOVABLY MOUNTED IN SAID HOUSING TO FORM A PUMP CHAMNER DEFINED BY A COMPLEMENTARY CIRCUMFERENTIAL DISCHARGE AND AN IMPELLER ENCLOSURE, SAID LINER WITH ITS FLANGES PARTIBLE ALONG THE SAME MEDIAL TRANSVERSE LINE AS SAID HOUSING, SAID LINER FLANGES FORMING THE SIDES OF SAID IMPELLER ENCLOSURE AND ON ON ONE SIDE CIRCUMSCRIBING THE INLET THERETO, COOPERATING COMPLEMENTARY SEATS LOCATED ON OPPOSED SURFACES ON EACH HOUSING AND LINER PART BETWEEN EACH FLANGE AND ITS CIRCUMFERENTIAL DISCHARGE TO HOLD SAID LINER PARTS IN MATING ENGAGEMENT WITH EACH OTHER ALONG SAID MEDIAL TRANSVERSE LINE WHEN SAID HOUSING PARTS ARE SECURED TO EACH OTHER BY SAID PRESSURE EXERTING MEANS, A RADIAL DISCHARGE IMPELLER HAVING AN INLET VORTEX ON ONE SIDE AND MOUNTED FOR ROTATION IN SAID IMPELLER ENCLOSURE AND HAVING PARALLEL SIDES RADIAL TO ITS ROTARY AXIS AND CLOSELY ADJACENT TO AND COEXTENSIVE WITH BUT SPACED FROM SAID LINER FLANGES, ANNULAR MARGINAL SURFACES DEFINING SAID LINER CIRCUMFERENTIAL DISCHARGE AND BEING FLUSH WITH THE CORRESPONDING INNER SURFACES OF THE RADIAL DISCHARGE SIDES OF SAID IMPELLER, ONE OF SAID LINER PARTS BEING MOVABLE FROM AROUND SAID MOUNTED IMPELLER WHEN THE OTHER PART OF SAID LINER AND HOUSING ARE REMOVED FROM SAID MEDIAL TRANSVERSE LINE. 